Hydraulically operated cycling device for a mining machine



Jan. 8, 1957 HYDRAULICALLY Filed Ayg. 28, 1952 FIG. 1.

E. J. OSTERHUS ET AL 2,776,824

OPERATED CYCLING DEVICE FOR A MINING MACHINE 1o Shets-Sheet I mvemons: I

ERVIN J. OSTERHUS ARCHER W. RICHARDS NORMAN W. TAYLOR ATTORNEY Jan. 8, 1957 E. J. OSTERHUS ET AL 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE l0 Sheets-Sheet 2 Filed Aug. 28, 1952 NNN ooooooo INVENTORS: I ERVIN J. OSTERHUS ARCHER w. RICHARDS N0 AN W.TAY OR ATTORNEY Jan. 8, 1957 5, os us ETAL 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE 1o Sheets-Sheet 5 Filed Aug. 28, 1952 FIG. 4.

FIG. 8. 33:4

. mvsmoas: ERVIN J. OSTERHUS ARCHER W. RICHARDS NORMAN W. TAYLOR ATTCRNEY Jan. 8, 1957 E. J. OSTERH-US ET AL 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE Filed Aug. 28, 1952 10 Sheets-Sheet 4 I I min II I s m D V S 0 4 WURR 4 62 A0 M fi @n 54 mD n w W NEwm 8 w 4 HR M fi 0w W IMRANH Wm m%MY j 4 WMRuR f E.AN Wm n V, 0 s m A w ATTO R N EY Jan. 8, 1957 E. J. OSTERRHUS ET AL 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE Filed Aug. 28, 1952 l0 Sheets'-Sheet 5 INVENTORS: ERVFN J. OSTERHUS ARCHER W. RICHARDS NORMAN W.- T YLOR ATTORNEY Jan. 8, 1957 E. J. O

STERHUS ET AL Q 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE Filed Aug. 28, 1952 10 Sheets-Sheet 6 FIG. 1

INVENTORS:

678 H6 19 Aw 'ERVIN J. OSTERHUS 7 {26 m m w ARCHER w. RICHARDS 676 l 7 NO AN w. TAYLOR M 4 I "m "m m. "WM )m- ATTORNEY Jan. 8, 1957 E. J. OSTERHUS ETAL 2,775,824

HYDRAULIC ALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE Filed Aug. 28, 1952 10 Sheets-Sheet '7 INVENTORS: ERVIN J. OSTERHUS. ARCHER W. RICHARDS RMAN W. TAYLOR ATTORNEY Jan. 8, 1957 E. J. OSTERHUS ET AL 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE Filed Aug. 28, 1952 l0 Sheets-Sheet 8 FIG. 27.

INVENTORS:

. ERVIN J. OSTERHUS r ARCHER W. RICHARDS RMAN W. AYLOR 2J6 B IF ATTORN EY 10 Shets-Sheet 9 E. J. OSTERHUS ET AL HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE Jan. 8, 1957 Filed Aug. 28, 1952 FIG. 32.

RMAN W. TAYLOR BY PM ATTORNEY mam M 4 0 4 2 W iwva z y w 2 7 6 lib? a U Wa A 6 w. 4' V M W M w f m a 7 i W 3 m will. h. 0 0 w v 2. 3 \l'l |1.1 8 1 p 4 V. w W% E 6 WfiMfiW A F w 68 Jan. 8, 1957 E, J, osT s T AL 2,776,824

HYDRAULICALLY OPERATED CYCLING DEVICE FOR A MINING MACHINE 1O Sheets-Sheet. 10

Filed Aug. 28, 1952 F ACCUMULATOR SIDESWING UPSWING INVENTORS: ERVIN J. OSTERHUS ARCHER W. RICHARDS I N RMAN W. TAYLOR BY PM ATTORNEY United States Patent HYDRAULICALLY OPERATED CYCLlNG DEVICE FQR A MHNING MACHINE Ervin J. Osterhus, Seven Hills Village, Archer W. Richards, Chagrin Falls, and Norman W. Taylor, Cleveland Heights, Ohio, assignors to Joy Manufacturing 101mpany, Pittsburgh, Pa a corporation of Pennsylvania Application August 28, 1952, Serial No. 306,854

32 Claims. (Cl. 262-29) This invention relates to mining machinery of the type known as continuous miners and shown in copending applications Serial Nos. 102,995 and 102,996, of l. D. Russell and J. R. Sibley, respectively, filed July 5, 1949, and Serial No. 201,411 filed December 18, 1950, of A. L. Barrett, all owned by the same assignee as the present application. More specifically, this invention relates to control means for moving the Vein-attaching and disintegrating instrument of the mining machine through a repeating cycle of operation. In its preferred embodiment, theinvention relates to means of this type which are substantially automatic.

As was pointed out in the above-identified Barrett application, it is hi hly desirablethat mining machines of the type referred to be made substantially automatic in their operation, for a number of reasons. One of these reasons is to remove the human element from bottom control and roof control in order to provide a more uniform bottom and roof, and in order to take out a maximum of coal or other mineral.

It is accordingly an object of this invention to provide means to operate a continuous mining machine through a repeating cycle with a minimum of human intervention. This and other objects are accomplished in control means made according to this invention, as will be set forth in detail below.

In the drawings:

Fig. 1 is a section on a horizontal plane through a portion of a mine showing a top plan view of a mining machine of the type referred to and equipped with this invention.

Fig. 2 is a View in section substantially on line 2-2 of Fig. l.

Fig. 3 is a top plan view of the cycling device itself, here shown with the cover removed.

Fig. 4 is a view in section substantially on line 4-4 of Fig. 3, but omitting the cam disconnect mechanism for the sake of simplicity.

Fig. 5 is a top plan View of a detail of the invention,

being a view in section substantially on line 5-5 of Fig. 4.

Fig. 6 is a View in section substantially on line 6-6 of Fig. 5. g I

Fig. 7 is a plan View of another detail, being substantially a view in section on line 7-7 of Fig. 4, turned through 90, and showing the cam disconnect mechanism omitted from Fig. 4.

Fig. 8 is another detail view of the portion shown in Fig. 7, being in effect a View from the plane of line 8-8 of Fig. 7 and looking in the direction of the arrows.

Fig. 9 is a view in section substantially on line 9-9 of Fig. 3.

Fig. 10 is an enlarged detail, being a plan view of that portion of the device shown substantially at the lower edge, and in the middle of that edge, of Fig. 3 and in cluding the two operating handles.

7 Fig. 11 is a view in section substantially on line 11-11 of Fig. 10.

Fig. 12 is a detail view of a portion of the device shown 'ice line 15-15 Fig. 17 is a view in section substantially on line 17-17 of Fig. 3, but with the overcenter device shown on dead center.

Fig. 18 is a view in section substantially on line 18-18 of Fig. 17. v

Fig. 19 is a view in section substantially on line 19-19. of Fig. 18.

Fig. 20 is a detail view, being a'side elevation view of the cam follower only, shown in Fig. 19 along with connected mechanism.

Fig. 21 is a view in section substantially on line 21-21 of Fig. 17 1 Fig. 22 is a View in section substantially on line 22-22 of Fig. 21.

Fig. 23 is a view in section through the toggle of the device shown in Figs. 17 and 18.

Fig. 24 is a view in section substantially on line 24-24,

of Fig. 17.

Fig. 25 is a view in section substantially on line 25-25 of Fig. 17, being in effect an extension of the upper end of Fig. 10 but on a slightly difierent scale than that of Fig. 10. I

Fig. 26 is a view in section substantially on line 26-26 of Figs. 3 and 27.

Fig. 27 is a top plan view of the detail shown in Fig. 26.

Fig. 28 is a view in elevation as seen from the left end of Fig. 26. i

Fig. 29 is a View in section on line 29-29 of Fig. 26. Fig. 30 is a view in section on line 30-30 of Fig. 27.

Fig. 31 is an enlarged detail view of one of the control No attempt will be made here to set forth the details.

of the continuous mining machine itself. It will suffice for the purpose of describing this invention to describe very briefly the mining machine to which this invention is applied, and to refer the reader for a more detailed description to the Russell and Sibleyapplications identified above. I I

Thus it will suffice to point out that a continuous mining machine to which this invention applies preferably comprises a caterpillar track mounted base 2 having a vein-attacking and disintegrating instrument 4 mounted for translatory movement with respect to the base .2,

for swinging movement about a horizontal axis substantially at the point 6 of Fig. 2, and for swinging movement about a vertical axis which is the axis of the turntable shown at 8 of Fig. 1. Mineral dislodged from the solid by the vein-attacking and disentegrating instrument 4 is carried by a conveyor 10 to a hopper 12, from which it is carried by a conveyor 14 to a discharge point 16 at the end of the machine.

Thus the vein-attacking and disintegrating instrument 4 is provided with three degrees of freedom, one of these being the reciprocatory movement or movement of translation, another being the swinging movement about the horizontal axis and the third being the swinging movement about the vertical axis. It will of course be understood by those skilled in the art that various means may be provided to effect movement of the instrument 4, but in the preferred embodiment of the invention, the desired movement is accomplished by means of hydraulic motors, and more specifically, hydraulic jacks.

Reference will be had to the above-identified Russell and Sibely applications for the details of the hydraulic jacks referred to and for their orientation withrespect to other elements of the machine, except for the vertical swing jacks, which are exposed and are shown at 18 of Figs. 1 and 2. The other jacks are indicated merely schematically in Fig. 34, and are furthermore indicated in Fig. 34 as a single jack in each case, whereas in fact each of the upswing, sump and sideswing jacks shown as single jacks at 18, 2t) and 22 of Fig. 34 is, in the preferred embodiment of the invention, two jacks working together, as will be understood by reference to the aboveidentified Russell and Sibley applications.

For a better understanding of the invention, Fig. 34 will be described in detail first, and the invention will thereafter be taken up in greater detail by reference to the otherfigures of the drawings. The valves shown diagrammatically at 24, 26 and 28 are the identical valves shown in the above-identified Russell and 'Sibley applications as being the manually operated upswing, sump, and sideswing valves. In this invention, these valves are not manually operated direc ly, but are connected for operation by valve operators 30, 32 and 34 respectively.

Each of the operators 30, 32 and 34 is preferably a spring-centered hydraulic motor, comprising acylinder 36, a piston 38, a piston rod 40 and suitable springcentering mechanism indicated generally at 42. The operator is connected in each case to operate its associated valve by means of any suitable linkage, shown in Fig. 34 schematically at 44. As will readily be understood by those skilled in the art, the valves 24, 26 and 28 are merely conventional open-center hydraulic control valves, the open-center passage being shown in Fig. 34 by lines 46, 48 and 50 respectively.

These three valves are shown in Fig. 34 in their centered positions. Operation of valve 28 into either of its two operating positions automatically interrupts fluid flow to valves 24 and 26; similarly, with valve 28 centered, the operation of'valve 24 counterclocl-zwise into one operating position automatically cuts off fluid flow to valve 26, but operation of valve 24 clockwise into its other operating position does not cut off fluid flow to valve 26 because of the bypass conduit 52.

Continuous mining machines of the general type shown in the patent applications identified above are provided with. any suitable source of hydraulic fluid under pressure, such as the pump shown schematically at 54-, which is connected directly by suitable conduit means with the bank control valves in the conventional arrangement, as will be understood by those skilled in the art upon reference to the Russell and Sibley applications aboveidentified. The pump receives fluid from'any suitable tank or reservoir 56 by means of a conduit 58. In this invention, instead of being directly connected by conduit with the bank of controlvalves, which would include valves 24,-26 and 28, the pump 54 is connected with the control valves throughan intermediate valve 60 by a conduit 62. Valve 60 may be any of a large number of suitableclosed-center valves, here shown as having four ports to one ofwhich is connected the conduit 62, a second of which is connected to a conduit 64 having therein a check valve 66, a third port which is connected with the conduit 68, and a fourth port towhich is connected a. conduit 70.

Conduit 64 also communicates with one of the ports of valve 28. Conduit 70 is connected with a metering device consisting of a hydraulic motor 72 of the piston and cylinder type, having a cylinder 74 and a piston 76 draulic system which makes up the control means.

reciprocable therein against a spring 73, and a piston rod 80 connected with the piston 76 and extending out through one end of the cylinder 74. A conduit 82 con nects conduit 64 with that end of cylinder 74 which is opposite the end with which conduit 76 is connected.

It was pointed out above that the operators 30, 32 and 34 for valves 24, 26 and 28 respectively are springcentered, with the result that valves 24, 26 and 28 are held in their centered positions when their respective operators are not provided with fluid under pressure. Valve 61) is not operated in the same manner, being provided with an operator 84 connected thereto by suitable linkage indicated generally at 86. Valve operator 84 is preferably a hydraulic motor, but unlike the operators 30, 32 and 34, is normally spring-biased toward one end of its travel rather than being spring-centered. Thus a spring 88 normally pushes the piston 90 of motor 84 to the extreme right end of cylinder 92 as seen in Fig. 34.

Control means for the valves 24, 26, 28 and 60 are provided, the control means operating of course directly upon the respective valve operators 3t 32, 34 and 84. The control means includes a plurality of valves, operators for those valves (not in each case shown in Fig. 34), snap acting mechanism (not shown in Fig. 34), a source of hydraulic fluid under pressure, and a cam mechanism. The control means is itself operated by metering mechanism which is associated with the means to supply hydraulic fluid under pressure to the upswing, sump, and sideswing motors 18, 20, and 22 respectively. Toward this end, means are provided to connect the control means for direction by the metering mechanism, the connecting means including a clutch and an actuator and an actuated element associated with the abovereferred to snap-acting mechanism.

More specifically, an accumulator 94 serves as an intermediate source of fluid under pressure for the hy- Accumulator 94 itself receives hydraulic fluid under pressure from pump 54 by means of a conduit 96 connected with conduit 62 and having therein a relief valve 98 and a check valve 100. Relief valve 98 is connected with tank 56 by means of a conduit 102.

Conduit 96 is connected, at a point between the accumulator 94 and the check valve 100, with another conduit 104, which has branch conduits 106 and 108 connecting with the several valves forming part of the control means.

One of the plurality of valves is connected to control movement through one degree of freedom, this being the valve shown schematically at 110. Valve 110 is a conventional two-position hydraulic valve having four ports, one of which is connected with conduit 108, a second of which is plugged as shown at 112, a third of which communicates with tank or reservoir 56 by a conduit 114,

and a fourth of which is connected with a conduit 116. Conduit 116 is provided with branch conduits 11S and 119, conduit 118 being connected with one port of another valve 120 in the control means. A second port of valve 120 is connected by means of a conduit 122 with the right end of cylinder 92 of the hyqdraulic motor 84. A third port of valve 120 is connected with reservoir 56 by means of a conduit 124. The remaining port of valve 120 is plugged as shown at 126.

Branch conduit 119 connects with one port of another valve 128 of the control means. A second port connects with conduit 106 by means of a branch conduit 130; a third port is plugged as shown at 132; and the remaining port connects with one end of a conduit 134, the

' other end of which connects with one port of still an a conduit 124 and the reservoir, and at the same time to connect conduit 118 with the plugged port, valve 128 is also turned through 90 in order to connect conduit 119 with the plugged port of valve 128 and in order to connect branch conduit 130 with valve 136 by way of conduit 134.

Valve 136 is a conventional three-position valve having four ports, one of which is connected with conduit 134 as aforesaid. A second port is connected by means of a conduit 146 with the right end of the cylinder of motor 34, and a conduit 142 connects another port of valve 136 with the left end of the cylinder of motor 34. The remaining port connects with the reservoir 56 by means of a conduit 144.

Valve 1356 determines the direction of sideswing. In the position shown in Fig. 34, valve 136 is in its neutral position. When valve 1.36 is turned counterclockwise into one of its two operating positions, conduit 134 communicates with the right end of motor 34 by way of conduit 140, while the left end of motor 34 communicates with reservoir 56 by way of conduits 142 and 144. Turning the valve clockwise into its other operating position communicates the left end of motor 34 with conduit 134 by way of conduit 142 while the right end of motor 34 is connected with reservoir 56 by way of conduits 140 and 144.

Branch conduit 11.36 is connected with one of thefour ports of another valve 146 of the control means. A second port is plugged as shown at 148, a third port is connected with reservoir 56 by means of a conduit 150,

and the remaining port is connected with still another valve 152 of the control means by a conduit 154. For automatic cycling, valve 146 is oriented in the position shown in Fig. 34. For manual control of the vein attacking and disintegrating instrument, valve 146 is operated by its internal spring (not shown) through 90 in order to connect conduit 106 with the plugged port 148, whereupon conduit 154 communicates with conduit 150 and reservoir 56.

Valve 152 has another port which connects with a -31 conduit 156, a third port connected with reservoir 56 by means of a conduit 158, and a fourth port connected with a conduit 160. Conduit 16% connects with one port of another valve 162 of the control means. A second port of valve 162 connects with a conduit 164, a third port connects with reservoir 56 by way of a conduit 166, and the remaining port connects with the right end of valve operator 311 by means of a conduit 168.

Conduit 156 connects with one port of another valve 170 of the control means. connects with the left end of valve operator 30 by means of a conduit 172, a th rd port connects with reservoir 56 by means of a conduit 174, and a fourth port connects with the right end of valve operator 32 by way of a conduit 176. The left end of valve operator 32 is connected with conduit 164 referred to above.

As was pointed out above, and as can be understood by reference to the above-identified copending applications on continuous miners, means are provided to supply hydraulic fluid under pressure to the hydraulic motors 18, 20 and 22, these supply means including the valves 24, 26 and 28 respectively. Valve 23 communicates with valve 24 by means of a conduit 178, while valve 24 is connected with valve 26 by means of a conduit 1851. A conduit 182 connects valve 26 with reservoir 56.

Valve 28 is connected with one end of the sideswing jack 22 by means of a conduit 184, and with the other end of sideswing jack 2?.- by means of a conduit 186. Upswing jack 18, being a single-acting jack, is connected to receive hydraulic fluid under pressure at one end only, this being by way of conduit 18% having therein a metering device 191) which, like the metering device 72 referred to above, is in effect a hydraulic motor having a very high efficiency. Hydraulic motor 190 is connected to A second port of valve 176 6 drive a plurality of actuators or cams 192, 194, and 196 through a clutch 198.

Upswing jacks 18 are connected to operate still another valve in the control means, this being the valve shown schematically at 269. More specifically, upswing jacks 18 are provided with a cam mechanism indicated generally (and schematically) at 202, cam mechanism 202 being connected by suitable linkage indicated generally at 204 to rotate valve 200 through 90 into its other operating position. Valve 2110 is preferably spring-biased by means not shown into the operating position shown in Fig. 34.

Valve 200 is a two-position valve having four ports, one of which is connected by means of a conduit 206 with conduit 188 at a point between the motor 190 and jack 18. A second port of valve 200 is plugged as shown at 207, a third port connects with reservoir 56 by means of a conduit 208, and the remaining port is connected to still another hydraulic motor 210 by means of a conduit 212. Hydraulic motor 210 is preferably of the piston and cylinder type and is provided with a spring 214 to keep the piston biased toward one end of the cylinder. Motor 210 operates means to disengage and re-engage clutch 198. The means to disengage and reengage clutch 198 include a clutch spring not shown in Fig. 34, a cam 216, and a cam follower 218.

Means are provided periodically to reorient the metering device 191) with respect to the control means, these reorienting means including the aforesaid cam element 192, a follower element 220, and means to engage the elements While the clutch 198 is disengaged, this means being the hydraulic motor 210. More specifically, the

follower element 220 is carried by piston rod 222 of motor 210; rod 222 also carries cam 216. Cam 192 is generally referred to as a heart-shaped cam, because of the recess 224 provided therein to receive the cam follower 220.

Cam 196, described above as being actuated or rotated by metering device 190 through the clutch 198, is connected to move valve 110 from the position shown in Fig. 34 through 90 into a position in which conduit matically at 226.

183 connects through valve 116 with conduit 116. The movement of the valve 110 by cam 196 is accomplished through the medium of a pusher element shown sche- In the actual connection, the pusher element 226 engages the stem of the valve through a resilient connection for reciprocatory movement, as will be described in detail below. In the schematic showing of Fig. 34, pusher element 226 acts through a rocker arm 226' and a link 226" to rotate the valve shown schematically at 110 in Fig. 34.

Valve 110 is returned from the operating position just referred to, to the position shown in Fig. 34 by means of a connection with the hydraulic motor or metering device 72. Again, this connection is merely shown schematically in Fig. 34 in order to indicate the desired function or result. As shown in Fig. 34, piston rod engages an arm 228 pivoted at 230 and provided with an adjustable abutment 232. In the actual structure, the pivot 230 is a rock shaft, as will be explained in detail below. As shown schematically in Fig. 34, arm 223 is connected with valve by means of linkage indicated generally at 234. The linkage 234, in the schematic showing, engages an arm 234 by means of a pusher element 236.

The means connecting the metering device with the control means also includes mechanism to disconnect cam mechanism 196 from valve 110. Such mechanism is desirable in order to insure that the continued rotation of cam 196 will not be impeded by interference on the part of the pusher element 226. The disconnect mechanism is of course shown schematically in Fig. 34, and includes a cam 238 mounted for movement by the hydraulic motor 72, preferably being carried by the piston rod 80. A cam follower 240 is mounted on a rocker arm 242 pivoted at 244. In the actual structure, the pivot 244 is" a rock shaft, as will be explained in detail below. The rocker arm 242 is connected to lift the pusher element 226 by means of a lifter element 246.

Sump jack 20 is connected to receive hydraulic fluid under pressure from, and to exhaust hydraulic fluid to, valve 26 by means of conduits 248 and 250 connected with the left and right ends of the sump jack respectively as seen in Fig. 34. In the conduit 250 there is provided a hydraulic fluid motor 252 which serves as a metering device and is of the same type of motor as the motor 190 associated with the upswing jack 18. Metering device 252 is connected to operate (in this case rotate) a cam 254.

Conduits 248 and 250 are connected by means of a connecting conduit 256 having'therein a relief valve 258. Relief valve 258 is designed to permit fluid flow in the direction of the arrow when the pressure exceeds a predetermined maximum. A similar relief valve 260 is connected into conduit 250 at a point between the metering device 252 and the sump jack, being disposed in a conduit 262 which connects with the reservoir 56. It may be pointed out here that the piston in the sump jack moves in the direction of the arrow for the sumpingin operationi. e., from right to left as seen in Fig. 34.

It may also be pointed out here that the control means, valves 110, 120, 128, 146, 152, 162, 170 and 200, are all conventional two-position, closed-center, four-port valves. Of these, valve 200 is spring-biased into the position shown in Fig. 34, and valve 146 is spring-biased into a position 90 from that shown in Fig. 34. Valve 136 is a three-position, closed-center valve with four ports.

The control means and connecting means are shown in the illustrated embodiment as being housed in a box indicated generally at 264 of Figs. 1 and 2. As is probably best shown in Fig. 3, the box 264 comprises a base plate 266 to which are secured in any suitable manner side plates 267, 268, 269, 270, 271, 272, 273, 274, 276 and 278. A cover plate 280 is preferably provided to complete the box.

Reference will now be had to the detailed views for a more complete description of the several parts of this invention. Fig. 4 is a side elevation view of the hydraulic motor 72. Hydraulic motor 72 is a positive displacement type of motor and serves as a metering device, providing a. closely controlled, measured quantity of fluid for operation of the sideswing jacks 22.

In the embodiment shown, metering device 72 is a high efiiciency hydraulic motor of the piston and cylinder type, having a cylinder 74 and a piston 76 reciprocable in the cylinder. A piston rod 80 is connected to the piston 76 and extends out through one end of the cylinder through suitable packing. The cylinder 74 is preferably hingedly mounted as shown at 282 to a block 284 secured in any suitable manner to the base plate 266.

In the description of this portion of the apparatus in connection with Fig. 34, it was pointed out that the piston rod 80 engages an adjustable abutment 232 near the end of the travel of piston 76. This is accomplished by means of an actuator 286 secured to piston rod 80 in any suitable manner, as for example by the threaded member 288.

It was further pointed out that the pivot 230 of arm 228 is actually a rock shaft, as is best seen in Figs. 4, 5 and 6. Arm 228 is secured to one end of rock shaft 230 for oscillation with the shaft. Rock shaft 230 is mounted for oscillation in suitable bearings 290 and 292. At the end opposite arm 228, an arm 294 is secured to oscillate with the rock shaft 230. Resilient means such as the spring 296 is provided, spring 296 being a helical spring having one end in engagement with arm 294 and its opposite end in. engagement with the base plate 266, with the resut that spring 296 biases rock shaft 230 counterclockwise as seen in Fig. 6 against a stop provided by another arm 298 secured to the rock shaft and having thereon an adjustable stop member 300. Stop. member 300 is adapted to engage the upper face of base plate 266 to limit the rotation of rock shaft 230 clockwise as seen in Fig. 4 (and counterclockwise as seen in Fig. 6, although arm 298 does not show in Fig. 6).

Arm 294 is connected to actuate pusher element 236 by means of linkage indicated generally at 234 and comprising a link 302, an arm 303 connected thereto and mounted to pivot about the axis of a rock shaft 304.

Rock shaft 304 carries another arm 306 in which the pusher element 236 is carried. Rock shaft 304 is mounted to oscillate in bearings 307 and 308.

A spacer sleeve 310 is secured to the outer end of piston rod by, for example, a set screw 312. Spacer sleeve 310 is axially adjustable on piston rod 80 and limits the rightward movement (as seen in Fig. 4) of piston rod 80 and piston 76 under the influence of spring 78 (for which see Fig. 34).

In the discussion of Fig. 34, reference was made to earn 238 and associated mechanism for disconnecting earn 196 from valve 110. For a complete understanding of this mechanism, reference is had to Figs. 7, 8, and 18. The rock shaft 244 referred to above is mounted for oscillation in bearings 314 and 316 mounted in bearing supports 318 and 320 respectively. To the end of rock shaft 244 opposite the cam follower 240, there is secured an arm 322. A link 324 is pivoted substantially midway between its ends about a pin 326 and is slotted at its ends. One of the slotted ends receives a pin 328 secured in the arm 322, and the other slotted end receives a pin 330 in the lifter element 246 referred to in the discussion of Fig. 34.

Lifter element 246 is preferably a bifurcated element having legs or bifurcations 332 and 334. The slot or space between the bifurcations 332 and 334 is occupied by a guide plate 336, which also serves as a vertical support, as will be seen below. Lifter element 246 further comprises a pair of plates 338 and 340 held in spaced apart relation by the aforesaid pin 330 and two additional pins 342 and 344 (Fig. 18). The pusher element 226 referred to in the discussion of Fig. 34 passes between the pins 342 and 344 and of course moves up and down with those pins as they move up and down with the lifter element 246.

Still another arm 346 is secured to the rock shaft 244, as by means of a set screw 348, and carries a pin 350. A spring 352 is mounted in tension between pin 350 and a suitable spring anchor 354 secured in any suitable manner to the base plate 266. Spring 352 comprises resilient means to bias the rock shaft 244 clockwise as seen in Fig. 8.

Reference will now be had to Fig. 9 for a detailed discussion and understanding of the valve operators 30,

32, 34- and their associated connections 42 and 44 with their respective valves. Inasmuch as operators 30, 32 and 34 are alike, it will suflice to describe one of them in detail. As can be seen in Fig. 9, the valve operator comprises a cylinder 36 having reciprocable therein a piston 38 (not shown in Fig. 9) to which is connected a piston rod 40. Piston rod 40 has associated with it a spring-centering device 42, referred to in the discussion of Fig. 34.

The spring-centering device comprises a cylindrical member 360 secured to and alined with the cylinder 36 as by a threaded member 362 having any suitable packing therein through which the piston rod 40 passes. Snap rings 364 and 366 are secured to the piston rod in spaced apart relation, and other snap rings 363 and 370 are secured to the interior of the cylinder member 360 and spaced apart by the same distance as the distance that spaces the snap rings 364 and 366. Spring seats 372 and 374 are provided, these spring seats being, in the 9 centered position of the valve operator, adjacent the snap rings 364, 368 and 366, 370 respectively. A centering spring 376 is disposed incompression between the spring seats 372 and 374.

Cylinder 36 is pivotally mounted at one end, as shown at 378, to the base plate 266. The same pivot mounting carries hingedly mounted links 380. The opposite ends of links 380 are joined by a pivot pin 384 which carries spaced apart connecting links 386 (Fig. 3). Piston rod 40 is pivotally connected with the links 386 by means of a pin 388, the connection with links 386 thus being between the ends thereof. At the ends opposite the pin 384, links 386 are joined by a pin 390 which also passes through one end of a link 392. To the other end of link 392 is secured the valve handle 394.

Reference will now be had to Figs. 10-14 for a discussion of the means for manual initiation of automatic operation when such operation is desired,'and for manual operation when that is desired. As there shown, manually operable means are provided to move the valve 146 and valves 120 and 128 from their operating posi tion in which control of the cycling is automatic into the operating position in which control of the cycling is manual.

To that end, an operating handle 3916, provided with a ball grip 398, is mounted to pivot about a horizontal axis provided by a pin 399 carried in a pedestal 400 mounted on base plate 266. It will be noted that the manually operable means of which handle 396 forms a part extends through a slot 401 of a plate 402. The ends of slot 401 are enlarged as shown at 403 and 403'. Plate 402 is secured to the edge of base plate 266 in any suitable manner.

Pin 399 is engaged by the bifurcations of a block 404 to which handle 396 is secured by means of a pin 406 and a connecting block 408. Pin 406 engages the block 404 pivotally to permit swinging of handle 396 about the axis of pin 406. Pin 406 carries at its outer end a downward depending link 410, to the lower end of which there is secured a protruding pin 412. Pin 412 engages a groove 414 of an actuator 416 secured to the stem 418 of valve 136.

As is best seen in Fig. 14, pin 412 is eccentric with respect to pin 406, with the result that oscillatory movement of handle 396 about the axis of pin 406 effects the actuation of valve stem 418 and the consequent operation of valve 136 between neutral and its two operating positions.

Still another pin 420 is carried in one of the bifurcations of the block, pin 420 being eccentric with respect to the pivot pin 399. The outer end of pin 420 carries one end of a link 422, to the other end of which is pivotally mounted an arm 424 by means of a pin 426. Arm 424 is rigidly secured to another arm 138 substantially midway between the ends thereof, arm 138 being pivotally mounted by means of a rock shaft 428. The arm 138 was first referred to in the discussion of Fig. 34 and comprises the mechanical interlock between the two valves 120 and 128. Arm 138 is slotted at its ends to engage pins in the stems 430 and 432 of valves 120 and 128 respectively.

'Rock shaft 428 is oscillatably mounted in bearings 434 and 436 (Fig. 10), these bearings being carried in suitable bearing supports mounted in any satisfactory manner on the base plate 266. Substantially midway between its ends, the rock shaft 428 carries secured thereto an arm 438. As is best seen in Fig. 13, arm 438 depends downward and is in position to engage the end of the stem 440 of valve 146.

At its left end as seen in Fig. 10, rock shaft 428 has secured thereto an arm 442. Arm 442 depends downward (Fig. 11) and engages at its lower end a link 4 44 by means of a pin 446. Between its ends, link 444 is provided with a downward depending pin 448 which engages a slot in a plate 450. Plate 450 is pivotally mounted on base plate 266 by means of a pivot member 452. An upward extending pin 454 is secured to plate 450 and engages one end of a link 456.

A pedestal 458 (Figs. 10 and 11) is suitably secured to the base plate 266, and provides near its upper end the socket of a ball and socket mounting, the ball being shown at 460 and being part of a universally jointed lever 462 carrying at its end a ball grip 464. The universal joint is shown at 466 and comprises a housing 468 which is preferably formed integral with ball 460 by means of a connecting sleeve 470. As seen in Fig. 11, the right-hand portion of lever 462 terminates at its left end in a mushroom type of head 472 which is normally in contact along its entire face with another mushroom type of head 474. The head 474 carries a stem 476 which passes through the hollow sleeve 470 and ball 460. A spring 478 biases the heads 474 and 472 to the right against a stop ring 480 held in place in the end of housing 468 by a snap ring 482.

The left end (as seen in Fig. 11) of stem 476 is adjacent a bearing plate 484 of an arm 486. Arm 486 is mounted to oscillate about the axis of rock shaft 428, this by virtue of the fact that arm 486 is secured to a sleeve 488 which surrounds the rock shaft 428 between the bearing 436 and the arm 438. Thus arm 486 is carried at the left end of sleeve 488 as seen in Fig. 10, and the right end of sleeve 488 carries still another arm 490. Arm 490 depends downward (Fig. 13) from sleeve 488 and is secured thereto in order to oscillate with sleeve 488. The lower end of arm 490 is adjacent the lower end of arm 438, so that arm 490 is also in position to engage the stem 440 of valve 146.

Ball 460 carries an upward extending projection 492, to the upper end of which are secured opposed transverse member 494 and 496. The outer end of member 494 passes through an opening in a link 498 which is held in place between washers 500 and 502, the washers being held against lateral displacement by any suitable means as, for example, by cotter pins 504. In a similar manner,

a link 506 is carried by the outer end of transverse member 496.

Reference was made above to better roof control and bottom control with the automatic cycling device than can be provided with manual control of the cycling. The means for accomplishing such control will be discussed in detail below. As will be understood by those skilled in the art, it is desirable to provide means for adjusting that portion of the control means which accomplishes the shifting of the valves at the desired roof and floor limits. What it amounts to is the provision of predetermined but variable limits. Fig. 15 shows a portion of the control means in which two manually operable handles, here shown as knobs, 508 and 510 are provided to permit the selective variation of the roof and floor or bottom limits. Thus the knob or hand wheel 508, being the upper knob, provides for variation of the roof control, whereas the lower knob or hand wheel 510 provides for variation of the floor or bottom control.

Knob 508 is mounted on a shaft 512 rotatable in a bearing 514 in the side plate 274. Shaft 512 connects With a universal joint indicated generally at 516, this joint being connected to turn a shaft 518. Knob 510 is mounted for rotation on and with a shaft 520 rotatable in a bearing 522 in side plate 274. Shaft 520 carries a sprocket wheel 524 which drives a sprocket wheel 526 through a chain 528. Sprocket wheel 526 is mounted for rotation with a shaft 530 which has at one end a bearing 531 in the side plate 274.

The means whereby the knobs 508 and 510 accomplish variation of the roof and bottom control will be pointed out in detail further on in this description.

' Reference is now made to Figs. 17-25 inclusive for a detailed description and understanding of the roof and bottom control mechanism forming part of the control means, and connections thereto. As there shown, valve 11 152lis connected for operation between its two. operating positions by snap-acting mechanism indicated generally at 532.. This connection includes a link 534 connected at its one end to the stem 536 of valve 152 and at its other end to the snap-acting mechanism.

More specifically, the snap-acting mechanism 532is 'of the over-center type, and comprises a toggle linkage which is preferably spring biased into either of its two overcenter positions. Thus, a pair of links 538. is pivotally mounted on the shaft 540 which is rotatable in bearings 542 and 544 provided in a U-shapedframe having u right members 546, 548 anda bottom member 556. The bottom member 550 is secured in any suitable manner to the base plate 266. The two links 538 pivotallyconnect with a link 560 by means of a pin 562, pin 562 constituting an actuated element for which the actuator is cam 194. Link 560 is mounted for pivoting or oscillation about the axis of stub shafts 564 which are in turn held in forward extending brackets 566 carried on one face of an upright mounting plate 336, first referred to above inthe discussion of Fig. 7 as a guide plate.

Thelink 560: carries a guide element 570which has a. sliding fit in the bore 572 of a cylindrical member 574. The cylindrical member 574 has an opening (not shown) in its upper end through which passes an extension 576 of the guide element 570. The extension 576 has 'a sliding fit in. the opening through which it passes, and is of a smaller diameter than the guide element 570. The annular space thus provided between the extension 576 and the bore 572 is occupied by a spring 578 which is com pressed between the upper face of guide element 570 and the upper end of the cylindrical element 574. A snap ring 580 fitting in a groove near the upper end of the extension 576 holds extension 576 against displacement through the opening in the top of cylinder 574.

Pin 562 carries one end of the link 498, the other end of which is 1 connected indirectly with the universally jointed lever 462; Pin 562 extends leftward as seen. in Fig. 17 sufliciently to be engageable by cam face 581 of the cam 194referred to above in the discussion of Fig. 34, more specifically in the discussion of the metering device 190. Cam 194- is mounted on a hub 582-which also carries a sun gear 584. The hub 582 and its gear 584 and cam l9-t'are rotatably. and slidably carried onthe shaft 540. A shifter arm 586 engages the hub 582 and provides means for shifting the cam 194 leftward into a position in which the cam 194 cannot engage pin 562.

Shifter arm 586 is carried on a hub 588 which is mounted for axial movement along a guide element 590. Hub 588 carries on its under side a pin 592.which is engaged by a slot 594 in a lever 596 pivotally mounted on a'pin 598 (Fig. 25).

The lever 596 carries at one end a pin 600 which is engageable in a slot 602 in a plate member 604. The

plate 604 is mounted for pivoting about the axis of a pivot pin 666 and is pivotally actuated by the link 444 first referred to above in connection with the description of Fig. 10, link 464 engaging theplate 604 by means of a pin 608.

At its outer end, lever 596 is slotted as shown at 610 to receive a'pin 612 extending downward froma block 613 secured by any suitable means on a shifter rod 614. Rod 614 is slidable in bearings 616 and 618, and carries a hub (indicated in phantomin Fig. 25) 620, the hub 620 carrying a shifter arm 622. Shifter arm 622 engages a hub 624. Hub 624 carries a sun gear 6 26 and the cam 196 first referred to in the above discussion of Fig. 34, more specifically in the description of upswing jacks 18 and associated metering device 190. v

Cam 136 is provided on one face t-hereof'with a wedgeshaped projection 628, projection 628 being adapted to engage an end of apin 638 secured in the lower ends "of the links 538. Pin'63tl engages both ofth'e pair 'oflinks 538 and projects to the right thereof as seen in Figs. 17 and 23. to permit engagement with the projection 628. Between the links 538, pin 630 is engaged by the valve including the shifter arm 622 be actuated, cam 196 will.

be shifted to the right by the axial displacement of hub 624 on shaft 540, into a position wherein the wedgeshaped projection 628 will not be capable of engaging the pin 630 because pin 630 will then be beyond the reach of projection 628.

As is best seen in Fig. 17, another sun gear 634 similar to but smaller than the sun gear 626 is keyed to shaft 540, as shown at 636. Sun gear 634 meshes with a somewhat larger planet gear 638 which is non-rotatably mounted on a hub 640. Hub 640 is rotatably mounted on a planet carrier 642 which in turn is mounted on a worm. gear 644. Worm gear 644 is rotatably mounted on shaft 540 by means of a bearing 646. The planet carrier 642.

preferably consists of an elongated member headed at one end as shown at 648 and threaded at the opposite end:

which passes through an opening in the worm gear 644.

A nut 650 engages the threaded end of the planet carrier.

and holds it on the worm gear 644.

Also carried on the hub 640 and non-rotatable with.

respect thereto is another planet gear 652, somewhat smaller than gear 638, planet gear 652 being positioned at all times to mesh with the axially movable sun gear 626. Gears 626 and 652 are always in mesh, regardless of the position of hub 624 on the shaft 540.

Reference was made above to the fact that sun gear 634 is keyed to shaft 540. In a similar manner, still another sun gear 654 is keyed to be driven by shaft 540. Sun gear 654 meshes with a planet gear 656 which is mounted on a planet carrier 658 and supported on a worm gear 660 in much the same manner as planet gear 638 is carried by planet carrier 642 and worm gear 644. Planet gear 656 is securely mounted on a hub which also carries another planet gear 662 so that gears 656 and 662 rotate together on a planet carrier 658. Gear 662 is always in mesh with sun gear 584, regardless of the position of gear 584 on shaft 540.

Worm gear 660 meshes with a worm 664 which is mounted on a shaft 666. Shaft 666 is mounted for rotation in suitable bearings in an upright support 668 and the above-identified upright support and guide 336. The bearing in the support 336 is shown at 670.

Shaft 666 is connected to be rotated by the drive shaft 518 through a universal joint indicated generally at 672. The shaft 518 is connected for rotation by the hand wheel 508 through the universal joint 516, as set forth in detail above in connection with the description of Fig. 15. In a similar manner, the worm wheel 644 meshes with a worm 674 which is carried on and rotated by the shaft 530, connected for rotation by the hand wheel 510. 1

Reference was made above (in the discussion of Fig. 34) of a pusher element, shown in Fig. 34 schematically, 226. The structure of pusher. element 226 is shown in detail in Figs. 18-20. As there shown, the pusher ele ment comprises a cam follower 676 hingedly mounted in a resilient connection 678 by means of a pin 680. Cam follower 676 is adapted to engage a cam face 682 formed by a notch. in the cam 196.

The resilient connection 678 comprises a hollow cupshaped element 684 in the closed end of which is provided an opening to receive the pin 680, and a slot to receive the cam follower 676. The hollow of the cup is formed by a relatively small bore 686 and a larger bore. 688. A hollow internally threaded bushing 690 is fitted in the small bore 686, and is slotted as shown at 692'to receive a pin 694 which holds the parts together. A

13 spring 696 is disposed in the annular space between the bore 688 and the bushing 690, the spring being initially compressed between the bushing 690 and the cup 684.

The internally threaded bore of bushing 690 is engaged by a similarly threaded portion of a valve stem 698. A lock nut 760 is provided on the threaded portion of the valve stem in order to hold the valve stem 698 and the bushing 696 in a preselected relationship. The valve stem 698 is the operating stem of the valve 110 discussed above in connection with Fig. 34.

The other end of valve stem 698 is operatively engaged by the pusher element 236, also referred to in the discussion of Fig. 34, and described in relation to the detailed operating mechanism in the discussion of Figs. 4, and 6. Thus the pusher element 226 operates the valve stem 698 from one operating position into its other operating position, and the pusher elernent 236 returns the valve stem and of course the valve to its original operating position. The operating position of valve 110 as shown in Figs. 5 and 6 is the same as the position shown in Fig. 34.

As is best seen in Fig. 18, the cam follower 676 extends through an opening 702 in the vertical support and guide member 336. Vertical support 336 also serves as a guide element for the lifter element 246. Lifter element 246 was first discussed in detail in the description of Figs. 7 and 8. As was there pointed out, the lifter elemnet 246 is a bifurcated element having legs or bifurcations 332 and 334. The elongated space 704 between the bifurcations receives the guide plate 336 to guide the vertical movement of lifter element 246. As was pointed out above in the description of Figs. 7 and 8, and as is best seen in Fig. 18, the leg 332 has spaced pins 342 and 344 passing therethrough, and the cam follower 676 passes through the space between the pins 342 and 344. Thus it will be evident that upward movement of lifter element 246 will bring pin 344 into engagement with the lower edge of cam follower 676, causing it to swing about the hinge pin 688 and lifting the left end (as seen in Fig. 18) out of engagement with cam face 682 of cam 196.

The shaft 546 shown in Figs. 17, 18, 21, 23 and 24 is connected to be driven by the metering device 190, discussed in the description of Fig. 34, through mechanism which will now be described and which is best shown in Figs. 26-30. Shaft 546 is non-rotatably connected with the external cone piece 786 of cone clutch 198 through the medium of cam 192, cam 192 being secured to the external cone piece 766 by any suitable means as by thev threaded members 788. Shaft 548 is securely held in the cam 192 in the embodiment shown by a set screw 710.

The internal cone piece 712 of the. clutch 198 is mounted for axial displacement on a hub 714. However, internal cone piece 712 and hub 714 are non-rotatable with respect to each other because of a key 716 engaging both the internal cone piece 712 and the hub 714. A spring 718 biases the internal cone piece 712 into engagement with the external cone piece 706.

A shifter yoke 728 engages a collar 722 on a hub 724 of the internal cone piece 712. Shifter yoke 720 pivots about the axis of a rock shaft 726 to which the shifter yoke is non-rotatably secured in any suitable manner.

. Shaft 726 is pivoted by the cam follower 218 referred to above, cam follower 218 being non-rotatably secured to shaft 726, as for example by means of the threaded member 728 engaging and clamping together two bifurcated portions of the cam follower 218.

Cam follower 218 is positioned for counterclockwise pivoting about shaft 726 as seen in Fig. 30, the pivoting action being accomplished by the cam 216 carried by piston rod 222. Piston rod 222 is actuated leftward as seen in Fig. 26 by a piston 730, piston 730 forming one element of the hydraulic motor 210 first referred to above in the description of Fig. 34.

Piston rod 222 also-carries the follower element 220 referred to above in the description of Fig. 34, follower 1 4 element 220 being adapted to engage the recess 224 of the heart-shaped cam 192.

The hub 714, which drives the internal cone piece 712 through the medium of key 716, is itself mounted on and driven by a shaft 732. Shaft 732 is driven or rotated by the metering device through the medium of enclosed reduction gearing 734, and additional reduction gears inv dicated generally at 736 (see Fig. 3 for gearing 734' and 736).

The control of fluid to operate the fluid motor 210 shown in Figs. 26 and 27 is provided by the valve 200 shown schematically in Fig. 34. The actual valve is shown in elevation in Fig. 31 with its actuating linkage. The location of valve 280 on the machine is best noted by reference to Fig. 2 where, because of the extremely small scale, valve 200 is merely shown as a small square at the back end of the sideboard 738 on the vein-attacking and disintegrating instrument.

As shown in detail in Fig. 31, valve 280 is itself mounted on a base plate 740 which is in turn mounted on the sideboard 738 by suitable fastening means 742. Operating linkage 744 is provided to cooperate with a cam 746 located on an adjacent stationary portion of the continuous mining machine. More specifically, the cam 746 is mounted on the pivot boss 748 for the veinattacking and disintegrating instrument, the pivot boss 748 being on the front conveyor frame.

The linkage744 comprises a pair of spaced parallel bar members 750 and 752, the forward bar member 758 being broken away in Fig. 31 in order to show the bar member 752 and other mechanism which would otherwise be obscured. The two bars 750 and 752 are spaced apart by a block 754 and a bushing 756, the bushing 756 receiving a pivot pin 758 which is secured in the base plate 746 in any suitable manner and which passes through the two bars 750 and 752 and through the bushing 756 as aforesaid. A snap ring 760 holds the assembled linkage against displacement off the pin 758. Block 754 is held in place between bars 750 and 752 by threaded members 761.

A single-acting (or one way) cam follower mechanism indicated generally at 762 is provided to make the actuation of valve 200 possible in only one direction of movement of the vein-attacking and disintegrating instrument. As shown, the cam follower mechanism 762 comprises a block 764 hingedly mounted between the bars 750 and 752 by means of a pin 766 secured in openings in the two bars and passing through the block 764. Block 764 carries a threaded adjustable stop member 768 near one end and near the other end carries a threaded adjustable cam follower element 770. Cam follower element 770 is held in place in the block 764 by a suitable set screw 772. A spring 774 keeps the cam follower mechanism 762 biased as far as possible counterclockwise as seen in Fig. 31, namely with the step 768 in engagement with bushing 756.

Block 754 is provided with a threaded opening to re ceive a threaded member 776 which is in position to actuate the valve stem shown schematically at 264 in Fig. 34 and shown again in Fig. 31 as the actual reciprocable operating stem of valve 200. It will of course be understood by those skilled in the art that the valve 209 is spring biased into the operating position shown in Figs. 31 and 34, the spring being mounted inside the housing of valve 200 and therefore not showing in Fig. 31.

It may be pointed out at this time that the schematic illustration Fig. 34 shows valve 200 as being operated in one direction by. cam mechanism associated with the upswing jack piston rod. In the actual structure, the cam is mounted on a stationary part of the machine, and the cam follower and associated operating mechanism are disposed on a moving partnamely on the vertically swinging vein-attacking and disintegrating instrument 4 the stationary cam and moving follower being sufliciently close together that relative movement in one direction operates the valve.

Reference is now made to Figs. 32 and 33, wherein is shown an over-center type of snap-acting mechanism very similar to the over-center type of mechanism shown in Figs. 17, 18 and 23, but in this case being associated with the sump jacks 20 and to that end being connected for operation by the metering device 252.

In view of the similarity of the two over-center devices, the one shown in Figs. 32 and 33 will not be described with the same detail as the oneshown in Figs. 17, 18 and 23. It will sufiice to point out that a toggle device indicated generally at 778 is mounted on fixed pivots 780 and 782 and has a moving pivot providing the snap action at 784, the lower portion of the toggle linkage carrying the pin 786 which, between the parallel links 788, engages a valve operating link 790 and at its end (right end as seen in Fig. 33) is in position to engage a projection 792 secured in the groove 794 of cam 254.

Cam 254 comprises an annulus 796 secured to a hub 798 which is axially movable on a sleeve 800 but is nonrotatable with respect thereto because of a key 802. Thus pin 786 is an actuated element, its actuator being cam 254 and the projection 792.

The sleeve 800 is mounted for rotation in bearings 804 and 806 in the upright supports808 and 810 respectively, uprights 808 and 810 forming a part of a rectangular frame having transverse members 812 and 814, the frame being secured in any suitable manner to the base plate 266.

The sleeve 800 is connected for rotation by the metering device 252, this connection including any suitable shaft engaging in non-rotating relationship the bore 816 of sleeve 800, enclosed gear reduction means 818 and additional gear reduction mechanism 820 (see Fig. 3 for elements 818 and 820).

The hub 798 is provided with a flange or collar 822 which is spaced from the annulus 796 to provide a groove which receives a shifter member 824. Shifter member 824 is secured by any suitable means to a hub 826 which is slidable axially on a support 828 mounted between the vertical supports 808 and 810 by means of threaded.

members 830. To the. underside of the hub 826 there is secured a pin 832 which receives the end of the link 456 first described in connection with Fig. 10. The left end of the moving pivot 784 carries the end of the link 506, link 506 also having been first referred to in the description of Fig. 10.

The link 790 referred to above engages the pin 786 as aforesaid by means of a rectangular recess 834, recess 834 being preferably longer than the diameter of the pin 786. Link 790 joins at one end the stem 836 of valve 170 by means of pin 838'and at its other end the stem 840 of valve 162 by. means of pin 842. Thus it will be seen that the valves 162 and 170 are mechanically interlocked so that when the stem of valve 170 is depressed, that of valve 162 is extended, and when the stem of valve 170 is extended, that of valve 162 is depressed.

OPERATION In discussing the operation of this invention as applied to a continuous miner of the type referred to herein, it will be assumed that the machine is starting with the vein-attacking and disintegrating instrument adjacent the floor, swung to one extreme position, as for example to the right as seen in Fig. l, and in the retracted position prepared to sump-in. The instrument 4 is, in other words, in the position A shown in Fig. 2 and swung way over to the right, i. e. clockwise about its vertical pivot, as seen in Fig. 1.

Automatic cycling This description of-the operation will first cover automatic cycling, for which the operating position of handle 396 is as shown in Fig. 14. With handle 396 in the position shown, valves 120, 128 and 146 are in the operating positions shown in Fig. 34, the stem of valve 146 being depressed against its spring by arm 438, shaft 428, arm 424, link 422, and block 404, of which block 404 is actuated by the handle 396 through connecting block 408 and pin 406.

The operating position of valve is also as shown in Fig. 34, but the position of this valve is not controlled by the position of handle 396. Similarly, the position of valves 152, 162 and 170 is determined by the fact that the vein-attacking and disintegrating instrument is fully retracted, is down adjacent the floor, and is thus ready to begin the sumping-in operation.

With the machine ready to sump-in, the universally jointed lever 462 is forward, namely in the position shown at B of Fig. 10. Valve 152 is in the operating position 90 from that shown in Fig. 34, while valves 162 and 170 are in the operating positions shown in Fig. 34. The operating position of valve 200 is not determined by the question of'whether or not the cycling is automatic.

The operating position of valve 136 is determined by the lateral position of the actuating knob 398 of handle 396-i. e., whether the knob 398 is in its neutral position, as shown in Fig. 16, to the right or to the left of its neutral position. Valve:136 in Fig. 34 is shown in its neutral position. The connections are preferably made such that the vein-attacking and disintegrating instrument will swing about its vertical axis from left to right when the knob 398 in Fig.- 16 is to the right of the position there shown, and conversely when knob 398 is to the left of the position shown in Fig. 16, the instrument 4 will swing from right to left about its vertical axis.

It will further be assumed that pump 54 has been operating and that accumulator 94 is fully charged. Fluid accordingly flows under pressure either from the pump 54 or from the accumulator 94 through conduits 104 and 106 to and through valve 146, through conduit 154 to valve 152, through valve 152 and conduit to valve 162, andthrough valve 162 and conduit 164 to the left end of the cylinder'of valve operator 32. At the same time, the right end of the cylinder of valve operator 32 is connected with the reservoir 56 by way of conduit 176, valve and conduit 174.

The piston of valve operator 32 is accordingly moved to the right as seen in Fig. 34, whereupon valve 26 is rotated clockwise through 45 connecting the conduit 180 with the conduit 250 through valve 26 and thus connecting the right ends of the sump jacks 20 with a source of supply of fluid under pressure, namely pump 54, by way of conduit 62, valve 60, conduit 64, valve 28, conduit 178, valve 24, conduit 180, valve 26, conduit 250 including motor or metering device 252, to the right ends of sump jacks 20. At the same time, the left ends of the sump jacks are connected through conduit 248, valve 26 and conduit 182 with the reservoir 56.

Fluidunder pressure accordingly flows through the metering device 252 into the sump jacks 20 at their right ends as seen in Fig. 34. Consequently, the instrument 4 is sumped into the. solid vein of coal or other mineral.

As oil (or other fluid) flows through the metering device 252, device 252, operating as a motor, rotates cam 254 untilthe projection 792 engages the pin 786 (Fig. 33). Continued rotation ofsthe cam causes the pin 786 to move and thus to snap the toggle over from its one operating positioninto the. position shown in Fig. 32. As the pin 786 snaps over, it carries link 790 with it, reversing the positions of valves 162 and 170 from the positions shown in Fig. 34 into positions 90 therefrom.

The position of valve 152 has not been changed, being still 90 from the position shown in Fig. 34. However, in the new operating position of valves 162 and 170, the left-end of thecylinder of operator 32 is connected with reservoir 56 by way of conduit 164, valve 162, and conduit 166. At the same time, the right end of the cylinder of operator 32 is likewise connected with the reservoir by way of conduit 176, valve 170, conduit 156, valve 152, and conduit 158.

At this time it is pertinent to consider the functioning of the apparatus in the event that the sump jacks 20 reach the end of their travel before cam 254 has tripped the toggle 778. If that happens, then of course the sump jacks can no longer receive any more hydraulic fluid. However, assuming now that the toggle 778 has not yet been tripped so that valves 162 and 170 are in the operating positions shown in Fig. 34, valve 26 is still oriented so as to admit fluid under pressure to the right ends of the sump jacks 20. Inasmuch as the sump jacks can take no more fluid, the pressure in the line 250 rises somewhat, and relief valve 260 opens. Accordingly, fluid continues to flow through the metering device 252 until the cam 254 has tripped the toggle 778, moving valves 162 and 170 into their operating positions which are 90 from the positions shown in Fig. 34. In these new operating positions, both ends of the cylinder of valve operator 32 are connected with reservoir 56 as outlined above. The centering device 42 of operator 32 accordingly centers the valve 26, trapping fluid in the sump jacks 20 and holding them in their fully extended position.

Meanwhile, fluid flows from the accumulator 94 or the pump 54 through conduits 104 and 106, valve 146, conduit 154, valve 152, conduit 160, valve 162 and conduit 168 to the right end of the cylinder of valve operator 30. The left end of the cylinder of valve operator 30 is connected with the reservoir 56 by way of conduit 172, valve 170, and conduit 17 4.

Valve operator 30 thereupon moves valve 24 from its centered position as shown in Fig. 34 to the operating position which is indicated schematicallyas being 45 counterclockwise from the position shown in Fig. 34. Fluid may now flow from pump 54 through conduit 62, valve 60, conduit 64, valve 28, conduit 178, valve 24, conduit 188 and motor or metering device 190 to the left end (as seen in Fig. 34) of the upswing jacks 18. Upswing jacks 18 are single-acting jacks, so this merely means that fluid enters the jacks and the instrument 4 begins to swing upward about its horizontal axis of swing.

As the jacks receive fluid, permitting hydraulic fluid to flow through the metering device 190, metering deiige 190 rotates cams 192, 194 and 196 through the clutch it must be explained at this time that, for upswing or upward movement in the vertical plane, the cam 196 rotates counterclockwise as seen in Fig. 34 and thus has no eifect whatever upon valve 110.

As the vein-attacking and disintegrating instrument 4 approaches a predetermined position (preferably approximately horizontal), cam follower mechanism 202 (Fig. 31) is brought into position so that the cam follower element 770 is engaged by the cam 746, swinging the linkage 744 counterclockwise as seen in Fig. 31, and operating valve 200 from the position shown in Fig. 34 against the bias of its enclosed spring (not shown) into the operating position 90 from that shown in Fig. 34.

Hydraulic fluid may now flow from conduit 188, where it is already under pressure, through conduit 206, valve 200 and conduit 212 to the hydraulic motor 210. Hydraulic motor 210 thereupon functions, and the first re sult of the functioning of motor 210 is the disengagement of clutch 198 by the cam 216 and cam follower 218. As the motor 210 continues to operate, the follower element 220 engages the recess 224 ofcam 192.

If the control means, metering device 190, and the upswing jacks 18 are in perfect synchronism, the recess 224 will be perfectly alined with the moving follower element 220. However, if there is some misalinement at this time, the follower element 220 will strike one side or the other of recess 224 and will re-orient the mecha nism to correct the misalinement. I

It will be remembered that the instrument 4 is mean- 18 while continuing its upward movement, so that the cam mechanism 202, including follower element 770, shortly clears the earn 746 and permits the internal spring of valve 200 to return that valve to the operating position shown in Fig. 34.

Motor 210 is thereupon connected with reservoir 56 by way of conduit 212, valve 200, and conduit 208, permitting the spring 214 to withdraw the follower element 220 and the cam 216. Clutch 198 is thereupon reengaged, and cams 192, 194 and 196 resume rotation.

Continued rotation of cam 194 results ultimately in the engagement of cam face 581 with pin 562, snapping the toggle mechanism 532'over and changing the operating position of valve 152 from what it was to the position shown in Fig. 34. The position of valves 162 and 176 is not changed by the throwing of toggle 532.

With the new orientation of the valves of the control means, the operator 30 has both ends of its cylinder connected with the reservoir 56, as follows: the right end of the cylinder by way of conduit 168, valve 162, conduit 160, valve 152 and conduit 158; the left end by way of conduit 172, valve and conduit 174. Accordingly, the operator 30 and valve 24 are returned to their centered position, trapping fluid in the upswing jacks 18 and holding them in their upper position.

With the new orientation of the valves of the control means just referred to, the operator 32 of the sump control valve 26 is connected as follows: the right end of the cylinder of operator .32 is connected with pump 54 or accumulator 94 by way of conduits 104 and 106, valve 146, conduit 154, valve 152, conduit 156, valve 170, and conduit 176; the left end of the cylinder of operator 32 is connected with the tank or reservoir through conduit 164, valve 162, and conduit 166.

With fluid being under pressure in the right end of the cylinder of operator 32, the piston of the operator moves to the left as seen in Fig. 34, turning valve 26 counter clockwise 45, and connecting conduit with conduit 248 through the valve. As a result, the left ends of sump jacks 20 as seen in Fig. 34 are connected with hydraulic fluid under pressure, while the right ends thereof are connected with the reservoir by way of conduit 250, valve 26 and conduit 182.

Accordingly, fluid flows into the sump jacks in such a manner as to effect retraction of the vein-attacking and disintegrating instrument 4. The fluid flowing through the tank from the exhausting ends of the sump jacks flows through the motor or metering device 252. This flow through metering device 252 drives or rotates the cam 254 until the projection 792 again engages toggle 778, snapping it over its dead-center position and reversing the operating position of valves 162 and 170. If it should happen that the sump jacks should be fully retracted before the toggle has been tripped, then the pressure in the conduit 24% will rise somewhat, and fluid will flow through relief valve 258 and conduit 256. This fluid will then flow through conduit 250 and the metering device 252 and will continue until the toggle 778 has been tripped, reversing the valves 162 and 170.

With this new orientation of the control means, the valves 152, 162, and 170 are all as shown in Fig. 34. 'Accordingly, both ends of the cylinder of operator 32 are connected with the reservoir as follows: the right end by way of conduit 176, valve 170, and conduit 174; the left end by way of conduit 164, valve 162, conduit 160, valve 152 and conduit 158. With both ends of the cylinder of operator 32 connected with the reservoir 56, the operator and its associated valve 26 are permitted to return to their centered position, trapping fluid in the sump jacks 20 and holding them in their retracted positions.

With valves 152, 162 and 170 oriented as above (and in this case as shown in Fig. 34), the cylinder of valve operator 30 is connected as follows: the left end is connected with fluid under pressure from accumulator 94 by way of conduits 104 and 106, valve 146, conduit 154,

19 valve 152, conduit 156, valve 170, conduit 172; the right end with the reservoir 56 by way of conduit 168, valve 162 and conduit 166. Accordingly, the piston of opera tor 30 moves to the right as seen in Fig. 34, turning the valve 24 clockwise through substantially 45, connecting conduit 1S8 directly with conduit 180.

The weight of the vein-attacking and disintegrating instrument 4 is sufficient to effect lowering thereof without the application of any hydraulic power. Accordingly, the weight of instrument 4 forces oil out of the upswing jacks by way of conduit 188 and metering device 199, valve 24, conduit 180, valve 26, and conduit 182 to the reservoir 56. The oil or other fluid leaving the jacks 18 must pass through the metering device 190, thus rotating the cams 192, 194 and 196. These cams will now rotate clockwise as seen in Fig. 34. Consequently, the rotation of earn 194 is of no consequence; similarly, the rotation of cam 192 is of no significance because the cam mechanism 202 is ineffective for the downward movement of instrument 4. However, the rotation of earn 196 is of significance in this phase of the operation.

As cam face 682 of cam 196 engages the pusher element 226, valve 110 is operated from the position shown in Fig. 34 counterclockwise through 90 to connect conduit 108 with conduit 116. Fluid then flows from accumulator 94 by way of conduits 104 and 103, valve 110, conduits 116 and 118, valve 129, and conduit 122 to the hydraulic motor 84, moving piston 99 thereof to the left as seen in Fig. 34 against the force of spring 88, and turning valve 69 counterclockwise through 90.

As a consequence, fluid under pressure is admitted to the hydraulic motor or metering device 72 as follows: from pump 54 through conduit 62, valve 60, and conduit 70. At the same time, a measured quantity of hydraulic fluid leaves the right end of cylinder 74 by way of conduit 82 and goes to the sideswing jacks 22 as will be pointed out below.

At the same time, that fluid under pressure is admitted to the hydraulic motor 84, fluid also passes to the valve operator 34 from conduit 116 by way of branch conduit 119, valve 128, conduit 134, and either conduit 140 or 142 depending upon the direction in which valve 136 has been pre-set by the manual control means consisting of handle 396 and ball 398. Assuming that valve 136 has been turned clockwise, fluid flows under pressure to the conduit 142, and thence to the left end of the cylinder of operator 34. Meanwhile, the right end of the cylinder of operator 34 is connected with the reservoir 56 by way of conduit 140, valve 136, and conduit 144. With the valve 136 thus oriented, the piston of operator 34 moves to the right, turning valve 28 clockwise as seen in Fig. 34 and connecting conduit 64 with conduit 184. Meanwhile, conduit 186 is connected with conduit 173 through valve 28, with the result that the right ends of the swing jacks 22 shown in Fig. 34 are connected with fluid under pressure and the left ends are connected to exhaust to the reservoir.

With valve 28 thus turned into an operating position, the metering device 72 discharges a measured quantity of fluid under pressure from its right end by way of conduit 82, and this fluid flows through conduit 64, valve 28, and conduit 184 to the right ends of the swing jacks 22, effecting side-swing of the vein-attacking and disintegrating instrument 4 about its vertical aXis.

The sideswinging movement continues until the actuator 286 (Fig. 4) on connecting rod 30 of the metering device 72 engages and moves adjustable abutment 232. This movement of adjustable abutment 232 pivots the arm 228 and the rock shaft 239 counterclockwise as seen in Fig. 4. As seen in Figs. 6 and 34, rock shaft 230 rotates clockwise, pivoting the arm 294 clockwise, which through the link 392 pivots the arm 303 counterclockwise. Accordingly, rock shaft 304, and arm 306 rotate counterclockwise as seen in Fig. 6, with the result that the pusher 20 element 236 returns valve 116 to the position shown in Fig. 34.

Hydraulic motor 84 is thereupon connected with the reservoir 56 by way of conduit 1Z2, valve 120, conduits 118 and 116, valve 110, and conduit 114. Spring 88 thereupon pushes the oil out of the cylinder 92, returning valve (iii to the position shown in Fig. 34, and permitting spring 78 to return piston 76 to the leftward limit of travel, substantially as shown in Fig. 34. However, this leftward movement of piston '76 does not take place until valve 28 has been returned to its centered position.

it will be recalled that the return of valve 110, referred to above, connects conduit 116 with conduit 114. Consequently, the left end of the cylinder of operator 34 is connected with the reservoir by way of conduit 142, valve 136, conduit 134, valve 128, conduits 119 and 116, valve 11% and conduit 1,14. The right end of the cylinder of operator 34 remains connected with reservoir 56 by way of conduit 140, valve 136 and conduit 144. With both ends of the cylinder connected with the reservoir 56, operator 34 and valve 28 return to their centered position.

It will thus be seen that the metering device 72 admits a measured or metered quantity of hydraulic fluid under pressure to the sideswing jacks illustrated schematically in Fig. 34 at 22. This measured quantity effects a predetermined but limited degree of sideswing, or swing about the vertical axis. After valve 28 has been returned to its centered position, the metering device '72 is returned to the orientation shown in Fig. 34 by its spring '73, in the course of which fluid is exhausted from the left end of cylinder 74 by way of conduit 70, valve 66 and conduit 68. The right end of cylinder '74 receives fluid, although at exhaust pressure, by way of conduits 6 6 and 8.2, with the result that metering device 72 is then ready for another sideswing cyclc.

Reference is made again to the portion of the operation in which piston rod starts its movement to the right as seen in Fig. 34. As rod 30 moves to the right, cam 238 engages cam follower 240, pivoting cam follower 240 and rock shaft 244 counterclockwise as seen in Fig. 8. Arm 322 also pivots counterclockwise, and pin 328 engages the pivoted arm 324 to pivot arm 324 clockwise as seen in Fig. 8, and to lift the lifter element 246. As lifter element 246 is raised by the action of arm 324, the pin 344 in the lower end of leg 332 of lifter element 246 (Fig. 18) engages the lower edge of cam follower 676, lifting it out of engagement with the cam face 682 of earn 196. Thus cam follower 676 is no longer in position to impede or interfere with the rotation of cam 196.

It will be recalled that we are still in that stage of the operation in which the vein attacking the disintegrating instrument 4 is lowering by its own Weight. The metering device continues to rotate earn 196 until pin 630 engages the wedge-shaped projection 628 (Figs. 21, 22 and 23), tripping the toggle mechanism 532 and switch ing valve 152. The machine is now ready to begin another cycle, having passed through the complete cycle of sump, upswing, retract, downswing, and, during the downswing operation, having indexed substantially the width of instrument 4 about its vertical axis of swing.

It will be noted that, with the handle 3% in the position for automatic operation, rock shaft 423 has been rocked clockwise as seen in Fig. 11, pivoting the arm 442 clockwise and moving the link 444 to the left as seen in Fig. 11, and toward the top of the sheet as seen in Fig. 10. As link 44 moves upward as seen in Fig. 10, pin 448 secured to the underside of link 444, pivots the plate 450 clockwise about its pivot 452, moving link 456 and pin 832 to the right as seen in Fig. 10, and to the left as seen in Fig. 33. The result is that the hub 826 and shifter arm 824 are moved leftward as seen in Fig. 33 to insure that the projection 792 is in position to engage the pin 736.

Similarly, upward movement as seen in Fig. 10 of link 444 pivots the plate 604 clockwise about its pivot pin 

